CN110168245A - Clutch unit and vehicle - Google Patents

Abstract

It is a kind of can by the construction different from the device of wear compensation proposed in the past, come cope with torque transmission member abrasion clutch unit.Clutch unit (17) includes clutch (13) with clutch spring (28), generates motor (50) for activating the actuating driving force of clutch (13), actuating driving force is transmitted to clutch (13) and receives the output shaft (63) of the elastic-restoring force of the clutch spring (28) as clutch reaction force and the auxiliary force for being used for assisted activation driving force is input to the spring (71) of output shaft (63).When clutch (13) is switched to discrete state from engagement state, auxiliary force is input to output shaft (63) before the input of clutch reaction force, and when clutch (13) is switched to engagement state from discrete state, auxiliary force becomes zero after clutch reaction force becomes zero.

Description

Clutch unit and vehicle

Technical field

The present invention relates to the clutch units that can transmit and disconnect torque.

Background technique

Known clutch unit includes that clutch and the power generated for activating clutch (hereinafter referred to as activate driving Power) actuator.Such clutch unit can be by using the actuating driving force generated by actuator, to make clutch exist Switch between engagement state and discrete state.The engagement state of clutch refers to the state of clutch transmission torque, and clutch The discrete state of device refers to through clutch the state for disconnecting torque.

Such clutch unit as described above has the known construction including secondary spring component, so as to by actuator The operation of switch clutch.For example, slip clutch disclosed in patent document 1 includes clutch engagement means, electronic horse It reaches, elastic ancillary equipment (helical spring) and connecting rod.

The clutch engagement means of slip clutch disclosed in patent document 1 include frictional disk, friction facing, fly Wheel, thrust plate and diaphragm.Friction facing is arranged between flywheel and thrust plate, and is supported on the peripheral part of frictional disk.Just Often in operation (when not from electric motor to diaphragm applied force), from diaphragm on thrust plate applied force.Friction facing position as a result, Between flywheel and thrust plate.Therefore, slip clutch disclosed in patent document 1 is engagement state in normal operation. In the following description, by not by power from actuator apply on the clutch when the clutch unit in engagement state it is referred to as normal Closed form clutch unit.

In slip clutch disclosed in patent document 1, diaphragm is connect by connecting rod with electric motor.For example, When slip clutch disclosed in patent document 1 is switched to discrete state from engagement state, by the actuating of electric motor generation Driving force is transmitted to diaphragm by connecting rod.Although detailed description is omitted, by connecting rod come by the central part of pressuring film plate. At this point, the peripheral part (part contacted with thrust plate) of diaphragm is mobile far from thrust plate.Thrust plate is applied to from diaphragm as a result, Power reduces.Therefore, thrust plate reduces relative to the pressing force of friction facing.As a result, slip clutch is in discrete state.

In slip clutch disclosed in patent document 1, other than the actuating driving force generated by electric motor, Connecting rod is also by the power (hereinafter referred to as auxiliary force) generated by elastic ancillary equipment.Hereinafter, it is briefly described referring to attached drawing The power generated in the slip clutch of patent document 1 by diaphragm, electric motor and elastic ancillary equipment.

Figure 15 is auxiliary by diaphragm, electric motor and elasticity in the slip clutch described in patent document 1 for describing The chart for the power for helping equipment to generate.In Figure 15, the longitudinal axis indicates the power being applied on connecting rod, and horizontal axis indicates the traveling of connecting rod Distance (travel distance of the contact portion between connecting rod and diaphragm).In Figure 15, curve C1 expression is applied on connecting rod from diaphragm Power (reaction force on connecting rod is applied to from diaphragm), curve C2 indicates the auxiliary that is applied on connecting rod from elastic ancillary equipment Power, and curve C3 indicates the actuating driving force being applied on connecting rod from electric motor.In Figure 15, indicate rubbing with positive value Formula clutch is switched to the power applied on the direction of engagement state, and is indicated to be switched to separation in slip clutch with negative value The power applied on the direction of state.Travel distance is 0 (zero) when slip clutch is switched to engagement state, and with even Bar moves on the direction that slip clutch is switched to discrete state and is increased.

As shown in figure 15, in slip clutch disclosed in patent document 1, connecting rod is applied in order to offset from diaphragm On reaction force (C1 of Figure 15), the auxiliary force generated by elastic ancillary equipment (C2 of Figure 15) is input on connecting rod.? That is when slip clutch is switched to engagement state or discrete state by electric motor, by elastic ancillary equipment The auxiliary force of generation as auxiliary electric motor power and be applied on connecting rod.As a result, in friction disclosed in patent document 1 In formula clutch, slip clutch can be switched to engagement state or discrete state by lesser actuating driving force.

In clutch unit, the component (hereinafter referred to as torque transmission member) of torque is transmitted with operation by frictional force The passage of time and wear.In slip clutch disclosed in patent document 1, the friction facing as torque transmission member It is worn with the passage of operating time.

In slip clutch disclosed in patent document 1, when friction facing abrasion, thrust plate is moved towards flywheel It is dynamic.The movement of thrust plate towards flywheel causes the shape of diaphragm to change.Joint shape is switched in slip clutch as a result, When state or discrete state, the size for the reaction force being applied on connecting rod from diaphragm changes.That is, with song in Figure 15 The size of power shown in line C1 changes.In this case it is necessary to which the actuating driving force generated by electric motor is (referring to figure 15 curve C3) size also change.When friction facing abrasion loss increase so that diaphragm significantly deforms when, need by The actuating driving force that electric motor generates also significantly changes.In order to cope with the variation of such power, need to be arranged with larger The electric motor of output.In this case, small-sized electric motor cannot be used, therefore the miniaturization of slip clutch becomes It obtains difficult.

In consideration of it, clutch engagement means are provided with for making up in slip clutch disclosed in patent document 1 The device (device of wear compensation) of abrasion.Device of wear compensation is configured to diaphragm when slip clutch is in engagement state Consistently maintain identical position.This is configured to the change for inhibiting the size for the reaction force being applied on connecting rod from diaphragm Change.

Reference listing

Patent document

Patent document 1: Japanese Unexamined Patent application publication (translation of PCT application): 2000-501826

Summary of the invention

Technical problem

Research of the inventor through the invention to closed type clutch unit, it is desirable that it is based on following reason, by using The construction different from device of wear compensation as described above, to cope with the abrasion of torque transmission member.

That is, if torque transfer can be coped with by the construction different from device of wear compensation as described above The abrasion of component, then the cost and size of clutch unit can reduce.

In consideration of it, can be by the construction different from the device of wear compensation proposed in the past it is an object of the invention to obtain Come cope with torque transmission member abrasion clutch unit.

The technical solution solved the problems, such as

The present inventor has carried out various grind to the abrasion of the torque transmission member in normal-close clutch device unit Study carefully.Specifically, carried out the research of the abrasion of torque transmission member to clutch unit, the clutch unit include: including The clutch of torque transmission member generates actuator for activating the actuating driving force of clutch, generates and be used for assisted activation The secondary spring component of the auxiliary force of device and the transmission member of clutch is transmitted to for driving force and auxiliary force will to be activated.? Abrasion in the research, to torque transmission member can be coped in the case where not compensating to the abrasion of torque transmission member Construction studied.

Clutch in normal-close clutch device unit is switched to engagement state by the present inventor's probe first Or when discrete state, in clutch, actuator and transmission member there is a phenomenon where.

As a result, when clutch is switched to discrete state from engagement state, due to the abrasion of torque transmission member, clutch Reaction force (such as the active force generated by clutch spring) becomes earlier at the time of being input to transmission member from clutch.More Specifically, discovery is when clutch is switched to discrete state from engagement state, the abrasion of torque transmission member leads to clutch Reaction force is input to transmission member from clutch before the auxiliary force generated by secondary spring component is input to transmission member. Therefore, after clutch reaction force starts to be input to transmission member from clutch, auxiliary force, which has occurred, cannot be used for activating The period of clutch.

On the other hand, when clutch is switched to engagement state from discrete state, due to the abrasion of torque transmission member, from The clutch reaction force that clutch is input to transmission member becomes later at the time of reaching zero.More specifically, discovery from When clutch is switched to engagement state from discrete state, the abrasion of torque transmission member causes to be input to transmitting from secondary spring component The auxiliary force of component just becomes zero before the clutch reaction force for being input to transmission member from clutch becomes zero.Therefore, Before the clutch reaction force for being input to transmission member from clutch becomes zero, the time that cannot use auxiliary force has occurred Section.

As described above, when torque transmission member abrasion, after the lock out operation of clutch starts and in clutch Bonding operation complete before, have occurred cannot use secondary spring component auxiliary force period.

Here, if the period that cannot use auxiliary force has occurred after the lock out operation of clutch starts, for Make clutch separation, needs to be generated biggish actuating driving force by actuator to cope with the clutch reaction force of clutch. In this case it is necessary to large-sized actuator, this is unfavorable in terms of the size reduction of clutch unit.

In addition, after the lock out operation of clutch starts and before the completion of the bonding operation of clutch, clutch Temporarily it is in half-clutch state.Particularly, when clutch is switched to engagement state from discrete state, clutch be in half from The period of conjunction state needs to accurately control clutch.However, when torque transmission member is worn as described above, in clutch Before the bonding operation of device is completed, the period that cannot use the auxiliary force of secondary spring component has occurred.When clutch is at this When period becomes half-clutch state, need accurately to adjust actuating while generating biggish actuating driving force by actuator Driving force.Due to being difficult to control actuator and it is necessary to provide large-sized actuators in this case, this is not Benefit.

In consideration of it, the present inventor has studied a kind of construction of clutch unit, even if the clutch unit is turning When square transmission member is worn, can also it prevent after the lock out operation of clutch starts and complete in the bonding operation of clutch At before, the generation of the period of auxiliary force cannot be used.As a result, inventor, which finally found that clutch unit only, needs structure as follows It makes.

Firstly, clutch unit is configured to when clutch is switched to discrete state from engagement state, auxiliary force is allowed to exist Before clutch reaction force is input to transmission member from clutch, transmission member is input to from secondary spring component.This In the case of, when clutch is switched to discrete state, even if clutch reaction force starts to be input to transmission member from clutch At the time of become earlier, clutch reaction force can also be inhibited just defeated from clutch before auxiliary force is input to transmission member Enter to transmission member.That is, even if torque transmission member is worn, can also inhibit to start it in the lock out operation of clutch Before, the generation of the period of auxiliary force cannot be used.

In addition, clutch unit only needs to be configured to, when clutch is switched to engagement state from discrete state, allow After the clutch reaction force for being input to transmission member from clutch becomes zero, transmission member is input to from secondary spring component Auxiliary force become zero.In this case, when clutch is switched to engagement state, even if being input to transmitting structure from clutch The clutch reaction force of part become at the time of reaching zero the auxiliary force that can also inhibit to be input to transmission member later from from The clutch reaction force that clutch is input to transmission member is reduced to zero before becoming zero.That is, even if in torque transfer It when component wear, can also inhibit before the bonding operation of clutch is completed, the generation of the period of auxiliary force cannot be used.

Based on aforementioned discovery, the present inventor has obtained following constructions.

Clutch unit according to an embodiment of the invention includes: clutch comprising is transmitted by frictional force Multiple torque transmission members of torque and the clutch spring that multiple torque transmission members are connected to each other by elastic-restoring force, The clutch allows hand over to transmit the engagement state of torque and disconnect the discrete state of torque；Actuator is generated for causing The actuating driving force of dynamic clutch；The actuating driving force generated by actuator is transmitted to clutch by transmission member, and from Clutch receives the elastic-restoring force of the clutch spring as clutch reaction force；With secondary spring component, will be used for The auxiliary force of assisted activation driving force is input to transmission member, wherein when clutch is switched to discrete state from engagement state, Auxiliary force is input to transmitting structure before clutch reaction force is input to transmission member from clutch, from secondary spring component Part, and when clutch is switched to engagement state from discrete state, it is anti-in the clutch for being input to transmission member from clutch After active force becomes zero, the auxiliary force for being input to transmission member from secondary spring component is become zero.

In clutch unit, when clutch is switched to engagement state or discrete state, transmission member not only receive from The clutch reaction force that clutch applies also receives the auxiliary force generated by secondary spring component.It will be from thus, it is possible to reduce Actuating driving force needed for clutch is switched to engagement state or discrete state.

When clutch is switched to discrete state from engagement state, before receiving clutch reaction force from clutch, Transmission member receives auxiliary force from secondary spring component.In this case, separation shape is switched to from engagement state in clutch When state, even if clutch reaction force becomes earlier at the time of being input to transmission member from clutch, clutch can also be inhibited Reaction force is input to transmission member from clutch before auxiliary force is input to transmission member.That is, even if torque passes Component wear is passed, is also possible to prevent before the lock out operation of clutch starts, the generation of the period of auxiliary force cannot be used.

In addition, when clutch is switched to engagement state from discrete state, from clutch be input to transmission member from After clutch reaction force becomes zero, the auxiliary force for being input to transmission member from secondary spring component is become zero.In such case Under, when clutch is switched to engagement state from discrete state, make even if the clutch for being input to transmission member from clutch is counter Become later, the auxiliary force for being input to transmission member can also be inhibited to be input to transmitting from clutch at the time of firmly reaching zero The clutch reaction force of component is reduced to zero before becoming zero.That is, even if in torque transmission member abrasion, it can also Before inhibiting the bonding operation in clutch to complete, the generation of the period of auxiliary force cannot be used.In this case, exist Period before the bonding operation completion of clutch, that is to say, that be in the period of half-clutch state in clutch, be not required to Biggish actuating driving force is generated by motor etc..Thereby, it is possible to easily adjust actuating driving force.

In the above described manner, in above-mentioned clutch unit, even if clutch can also be suitable when torque transmission member abrasion It is switched to engagement state or discrete state freely to cope with abrasion in the case where not compensating to abrasion.

On the other hand, clutch unit according to the present invention preferably includes following construction.In the mill of torque transmission member In the state that damage amount reaches preset limit, when clutch is switched to discrete state from engagement state, auxiliary force is anti-in clutch Active force from secondary spring component is input to transmission member before being input to transmission member from clutch, and clutch from point When being switched to engagement state from state, after the clutch reaction force for being input to transmission member from clutch becomes zero, from The auxiliary force that secondary spring component is input to transmission member becomes zero.

Even if clutch can also swimmingly switch as a result, when the abrasion loss of torque transmission member reaches preset limit For engagement state or discrete state.

On the other hand, clutch unit according to the present invention preferably includes following construction.In clutch from engagement state When being switched to discrete state, after clutch reaction force starts to be input to transmission member from clutch, from secondary spring structure The auxiliary force that part is input to transmission member is maximum.

In general, the predetermined amount of time after the lock out operation of clutch starts soon, is input to transmitting structure from clutch The clutch reaction force of part increases with the progress of the lock out operation of clutch.On the other hand, in above-mentioned construction, from Clutch reaction force starts after being input to transmission member from clutch, and auxiliary force is maximum.Even if being input to as a result, from clutch It, can also be defeated to transmission member when the clutch reaction force of transmission member increases with the progress of the lock out operation of clutch Enter enough auxiliary forces.As a result, clutch swimmingly can be switched to discrete state from engagement state.

On the other hand, clutch unit according to the present invention preferably includes following construction.In clutch from discrete state When being switched to engagement state, before the clutch reaction force for being input to transmission member from clutch becomes zero, from auxiliary bullet The auxiliary force that spring component is input to transmission member is maximum.

Period before the bonding operation of clutch is completed as a result, that is, when clutch is in half-clutch state Between section, enough auxiliary forces can be inputted to transmission member.It, can be with as a result, be in the period of half-clutch state in clutch The bonding operation of clutch is swimmingly executed using lesser actuating driving force.

Vehicle according to an embodiment of the invention includes the clutch unit with above-mentioned any construction.

Terms used herein are used only for the purpose of describing specific embodiments, and are not intended to the limitation present invention.

As it is used herein, term "and/or" includes any and all of one or more of related listed item Combination.

It will be further understood that, when used in this manual, the terms "include", "comprise" or " having " and its deformation are really Fixed stated feature, step, operation, the presence of component, assembly unit and/or its equivalent, but be not excluded for it is one or more its The presence of his feature, step, operation, component, assembly unit and/or combination thereof is additional.

Will be further understood that, term " installation ", " connection ", " connection " and/or its equivalent with broad sense using and including It directly or indirectly installs, connect and couples.In addition, " connection " and " connection " is not limited to physics or mechanical connection or connection, and It may include being electrically connected or coupling, it is either direct or indirect.

Unless otherwise defined, all terms (including technical and scientific term) used herein have and institute of the present invention The identical meaning of the normally understood meaning of the those of ordinary skill in category field.

It will be further understood that, such as those terms defined in common dictionary should be interpreted as having to it in related neck The consistent meaning of meaning in the context of domain and present disclosure, and will not be interpreted that ideal or excessive form is anticipated Justice, unless explicitly defining herein.

When describing the present invention, it should be appreciated that disclose many technologies and step.Each of these technologies and step All there is individual benefit, and each can also with one or more of the other disclosed technology or in some cases with institute There are other disclosed technologies to be used in combination.

As a result, for the sake of clarity, this specification will avoid each possibility that each step is repeated with unnecessary pattern Combination.However, this is read under should be in the range of understanding these combinations completely in the present invention and claims the case where Specification and claims.

Herein, the embodiment of clutch unit and vehicle according to the present invention is discussed.

In the following description, for illustrative purposes, numerous specific details are set forth in order to provide to of the invention thorough Understand.It is apparent, however, to one skilled in the art, that this can be practiced without these specific details Invention.

Present disclosure is considered as example of the invention, it is no intended to be limited the present invention to by the following drawings or description Shown in specific embodiment.

Beneficial effects of the present invention

It can be by different from the device of wear compensation proposed in the past according to the clutch unit of one embodiment of invention Construction cope with the abrasion of torque transmission member.

Detailed description of the invention

Fig. 1 be include first embodiment according to the present invention clutch unit vehicle side view.

Fig. 2 (A) is the partial sectional view for showing the schematic configuration of clutch unit, and Fig. 2 (B) is to schematically show Actuator rotates the exemplary chart of the relationship between angle and shaft torque.

Fig. 3 is the partial sectional view for showing the schematic configuration of clutch unit.

Fig. 4 is the partial sectional view for showing clutch drive apparatus in the way to enlarge.

Fig. 5 is the exploded perspective view of the auxiliary body and friction mechanism in clutch drive apparatus.

Fig. 6 is the view of the auxiliary body when the axis of output shaft looks up.

Fig. 7 shows the region X and Y in auxiliary body and corresponds to Fig. 6.

Fig. 8 schematically shows the example of the operation of auxiliary body.

Fig. 9 is the exemplary chart for schematically showing the relationship between actuator rotation angle and shaft torque.

The view of engine and clutch unit when Figure 10 is from vehicle up direction.

The view of engine and clutch unit when Figure 11 is from vehicular sideview.

Figure 12 is the cross-sectional view for showing friction mechanism in the way to enlarge.

Figure 13 is the perspective view for showing the construction of rotation transfer part and rotary body.

Figure 14 is the view for showing the schematic configuration of the clutch unit according to another embodiment and corresponding to Fig. 3.

Figure 15 is for describing to be set in usual technology by diaphragm, electric motor and the elasticity auxiliary in slip clutch The chart of standby generated power.

Specific embodiment

The embodiment of the present invention is described below with reference to the accompanying drawings.The size of component in attached drawing does not indicate component strictly Actual size and component dimension scale.

<overall construction>

Fig. 1 be include first embodiment according to the present invention clutch drive apparatus 14 vehicle 1 schematic diagram.Vehicle 1 is, for example, motorcycle and including vehicle body 2, front-wheel 3 and rear-wheel 4.Vehicle body 2 includes unshowned frame.For to The engine unit 10 that rear-wheel 4 provides rotary driving force is attached to the frame of vehicle body 2.

Engine unit 10 includes engine 11, speed changer 12 and clutch unit 17.Clutch unit 17 includes clutch Device 13 and clutch drive apparatus 14.Clutch 13 is constructed to be permeable to transmit the rotation of the unshowned crank axle of engine 11 To speed changer 12.That is, clutch 13 is constructed to be permeable to the rotation of crank axle is being transmitted to speed changer 12 and will not be bent The rotation of arbor, which is transmitted between speed changer 12, to be switched.

Fig. 2 (A) and Fig. 3 is the partial sectional view for showing the schematic configuration of clutch unit 17.Fig. 2 (B) and Fig. 9 is to show The view of the generated shaft torque in the output shaft 63 of aftermentioned clutch unit 17 is shown to meaning property.Fig. 3 and Fig. 9 are respectively The enlarged drawing of Fig. 2 (A) and Fig. 2 (B).The description of Fig. 9 will be provided below.

As shown in figure 3, clutch 13 is arranged on main shaft 15.Main shaft 15 is, for example, the input shaft of speed changer 12.Clutch 13 include clutch outer member 21 and the clutch inner core 25 being arranged in clutch outer member 21.

Clutch outer member 21 is in bottomed tube comprising for the perforative bottom 21a of main shaft 15 and the outer of bottom 21a is arranged in The tubular peripheral wall portion 21b in week.Bottom 21a and peripheral wall portion 21b is integrally formed.Clutch outer member 21 and main shaft 15 are coaxially disposed.From Clutch inner core 25 is arranged in the peripheral wall portion 21b of clutch outer member 21.

The bottom 21a of clutch outer member 21 is connected to reduction gearing 22.Reduction gearing 22 and the gear of crank axle (do not show It engages out), to be rotated together with the gear.Clutch outer member 21 and reduction gearing 22 are rotated according to the rotation of crank axle, And it can be rotated relative to main shaft 15.

Clutch inner core 25 includes clutch boss 26, pressure member 27 and clutch spring 28.Clutch boss 26 is in Column, and main shaft 15 runs through the columnar center.26 spline of clutch boss is connected to the peripheral surface of main shaft 15.As a result, Clutch boss 26 rotates together with main shaft 15.

Clutch outer member 21, clutch boss 26 and pressure member 27 are relative to main shaft 15 along the axial from one of main shaft 15 End is sequentially arranged.The axially external of main shaft 15 is arranged in pressure member 27, in the axis of main shaft 15 clutch boss facing upwards 26.Between clutch boss 26 and pressure member 27, multiple clutch disc 23 and multiple friction plates 24 are in the axial direction alternately Arrangement.Clutch disc 23 and friction plate 24 correspond to torque transmission member.

Friction plate 24 is arranged in the inner peripheral surface of clutch outer member 21, can rotate together with clutch outer member 21. Friction plate 24 can be rotated relative to clutch boss 26 and pressure member 27.

Clutch disc 23 is arranged in the peripheral surface of clutch boss 26, can revolve together with clutch boss 26 Turn.Pressure member 27 can rotate together with clutch boss 26.Clutch disc 23 can revolve together with pressure member 27 as a result, Turn.Clutch disc 23 can be rotated relative to clutch outer member 21.

Pressure member 27 can move in the axial direction relative to clutch boss 26.Clutch spring 28 is arranged in axial direction On towards clutch boss 26 push pressure member 27.Be arranged in as a result, between clutch boss 26 and pressure member 27 from Clutch piece 23 and the backup each other of friction plate 24.That is, clutch spring 28 connects clutch disc 23 and friction plate 24 each other It connects.In the state of above-mentioned clutch disc 23 and friction plate 24, the friction between clutch disc 23 and friction plate 24 makes clutch Boss 26 and clutch outer member 21 rotate together.The state is the engagement state of clutch 13.

Central part of the push rod 29 in the axial direction of pressure member 27.Push rod 29 is oriented to be extended in the axial direction.Push rod 29 Axial direction on one end be provided with flange part 29a.The other end in the axial direction of push rod 29 is connected by aftermentioned link mechanism 16 To clutch drive apparatus 14.Push rod 29 is constructed to be permeable to move in the axial direction by the output of clutch drive apparatus 14. In the case where push rod 29 is mobile along the direction (in Fig. 3 to the right) far from main shaft 15 in the axial direction, the flange part 29a of push rod 29 exists It is applied a force upon on pressure member 27 in axial direction along the direction far from clutch boss 26.As a result, clutch spring 28 deformation with It is compressed, so that pressure member 27 presses clutch disc 23 and the power of friction plate 24 reduces.

As a result, the contact pressure between friction plate 24 and clutch disc 23 reduces.As a result, friction plate 24 and clutch disc 23 Between engagement be cancelled, and clutch boss 26 and clutch outer member 21 rotate relative to each other.The state is clutch 13 discrete state.

That is, by the movement of push rod 29 in the axial direction, clutch 13 is cut between engagement state and discrete state It changes.

Pressure member 27 can be rotated by bearing 27a relative to push rod 29, and bearing 27a is between pressure member 27 and push rod Between 29.As a result, under the engagement state of clutch 13, pressure member 27 and clutch outer member 21 and clutch boss 26 are together Rotation.

(link mechanism)

As shown in Fig. 2, link mechanism 16 includes rotary shaft 31 and arm 32.Link mechanism 16 drives aftermentioned clutch The output of device 14 is transmitted to the push rod 29 of clutch 13.

One end in the axial direction of rotary shaft 31 is connected to the other end in the axial direction of push rod 29.Specifically, push rod 29 The other end in axial direction is provided with tooth-strip part 29b, and tooth-strip part 29b has the multiple teeth arranged in the axial direction.Rotary shaft 31 has With tooth-strip part 29b meshed gears 31a.

By above-mentioned construction, the rotation of rotary shaft 31 is so that push rod 29 moves in the axial direction.That is, 29 basis of push rod The direction of rotation of rotary shaft 31 moves back and forth in the axial direction.

For example, rotary shaft 31 is rotatably supported on the shell 20 for accommodating clutch 13 and speed changer 12.

Arm 32 includes the first arm 33, the second arm 34 and regulating mechanism 35.Each of first arm 33 and the second arm 34 Be formed as the plate extended in one direction.First arm 33 is connected to rotary shaft 31, can rotate together with rotary shaft 31. Second arm 34 is connected to the output shaft 63 of clutch drive apparatus 14, can rotate together with output shaft 63.First arm, 33 He Second arm 34 is connected to each other by regulating mechanism 35.

The rotation of the output shaft 63 of clutch drive apparatus 14 is transmitted to rotary shaft 31 by arm 32.Arm 32 will be from clutch The driving force that the output shaft 63 of device driving device 14 exports is transmitted to clutch 13, and will be by the clutch in such as clutch 13 The reaction force (hereinafter referred to as clutch reaction force) that device spring 28 generates is transmitted to the output shaft of clutch drive apparatus 14 63.That is, the clutch reaction generated in the output of the reception clutch drive apparatus 14 of output shaft 63 and clutch 13 Power.

First arm 33 and the second arm 34 are connected to each other by regulating mechanism 35, so that the distance between these arms are adjustable 's.Specifically, regulating mechanism 35 includes the first adjustment means 91, the second adjustment means 92 and adjusting bolt 93.

First adjustment means 91 are rotatably connected to the first arm 33.Second adjustment means 92 are rotatably connected to second Arm 34.That is, the first adjustment means 91 and the second adjustment means 92 are respectively by one end respectively with the bar of spherical portion Shape connecting elements 94 and 95 and be rotatably connected to the first arm 33 and the second arm 34.

The spherical part of connecting elements 94 and 95 is in the first adjustment means 91 and the second adjustment means 92.Connecting elements 94 Extend from the first adjustment means 91 towards the first arm 33, and is fixed to the first arm 33 while running through the first arm 33.Connection Component 95 extends from the second adjustment means 92 towards the second arm 34, and the second arm is fixed to while running through the second arm 34 34。

Adjusting bolt 93 is in the column extended in the axial direction.Both ends of the bolt 93 in the axial direction for adjusting bolt 93 are adjusted to have There are threaded portion 93a and 93b, and threaded portion 93a and 93b have helicla flute.When from the flighting front end of threaded portion 93b, Thread groove extends from the direction that the flighting front end in the 93b of threaded portion extends and thread groove from the flighting front end in the 93a of threaded portion It is contrary.Adjusting bolt 93 includes the large-diameter portion 93c in central part in the axial direction for adjusting bolt 93, and large-diameter portion 93c has the diameter bigger than the diameter of other parts.Large-diameter portion 93c is used as the maintaining part that rotation adjusts bolt 93, as described later.

First adjustment means 91 and the second adjustment means 92 have threaded hole 91a and 92a.When the opening from threaded hole 92a When the observation of end, the direction and thread groove that thread groove extends from the open end in threaded hole 92a are prolonged from the open end in threaded hole 91a That stretches is contrary.The threaded portion 93a of the one end being arranged in the axial direction for adjusting bolt 93 is screwed in threaded hole 91a.Setting The threaded portion 93b of the other end in the axial direction for adjusting bolt 93 is screwed in threaded hole 92a.Therefore, the first adjustment means 91 It is connected to each other with the second adjustment means 92 by adjusting bolt 93.

As described above, helicla flute in threaded portion 93b and threaded hole 92a with threaded portion 93a and threaded hole 91a extension Contrary side upwardly extends.Therefore, bolt 93 is adjusted relative to the first adjustment means 91 and the second adjustment means 92 with one The rotation of kind mode increases the assembly length for adjusting bolt 93 relative to the first adjustment means 91 and the second adjustment means 92.Separately On the one hand, it adjusts bolt 93 and tune is reduced with the rotation of opposite way relative to the first adjustment means 91 and the second adjustment means 92 Save assembly length of the bolt 93 relative to the first adjustment means 91 and the second adjustment means 92.Thus, it is possible to adjust adjusting bolt Position of the 93 threaded portion 93a and 93b relative to the threaded hole 91a and 92a of the first adjustment means 91 and the second adjustment means 92. That is, the first adjustment means 91 and the second adjustment means 92 are connected to each other to so that the first adjustment means 91 and second are adjusted The distance between component 92 can be adjusted by adjusting bolt 93.

First adjustment means 91 and the second adjustment means 92 can adjust bolt 93 by the way that nut 96 and 97 to be fastened to Threaded portion 93a and 93b and be fixed to adjust bolt 93 on, wherein between the first adjustment means 91 and the second adjustment means 92 Distance is adjusted by adjusting bolt 93.

The construction of regulating mechanism 35 as described above makes it possible to adjust the first adjustment means 91 and the second adjustment means 92 Between that is the distance between the first arm 33 and the second arm 34.Clutch 13 is relative to clutch drive apparatus 14 as a result, Operation and activate at the time of can change, be described further below.That is, for example, separation relative to clutch 13 Beginning, when clutch 13 is switched to discrete state from engagement state, can pass through regulating mechanism 35 adjust link mechanism 16 In the first arm 33 and the second arm 34 distance, auxiliary force is transmitted to clutch 13 from clutch drive apparatus 14 to change Moment.

(construction of clutch drive apparatus)

The construction of clutch drive apparatus 14 is described now with reference to Fig. 3 to Figure 11.Clutch according to this embodiment Driving device 14 exports and the auxiliary force of auxiliary body 70 to be added to the output of motor 50 (actuator) to clutch 13 The driving force of acquisition.

Fig. 4 shows the schematic configuration of clutch drive apparatus 14 in the way to enlarge.As shown in Figure 3 and Figure 4, clutch Device driving device 14 includes shell 40, motor 50, transmission mechanism 60, auxiliary body 70 and friction mechanism 80.

Shell 40 includes housing body 41, lid 42 and motor chamber 45.Fig. 5 is to show the clutch driving in decomposing state The exploded perspective view of a part of device 14.As shown in figure 5, housing body 41 is in the bottomed tube axially extending along cylinder.? That is housing body 41 has opening 41a.As shown in Figure 3 and Figure 4, housing body 41 accommodates transmission mechanism 60 and auxiliary machine Structure 70.As shown in figure 5, protruding portion 46 is formed on the bottom of housing body 41.

As shown in figure 4, lid 42 covers the opening 41a of housing body 41.There is storage space V in lid 42.Friction mechanism 80 It is arranged in storage space V.Lid 42 includes lid main body 43 and storage cover 44.Lid main body 43 has constitute storage space V one The first partial groove 43a.Storing cover 44 has the second groove 44a for constituting storage space V.It is covered in lid main body 43 and storage In the case that portion 44 combines, the first groove 43a and the second groove 44a constitute storage space V.

The output shaft 63 of aftermentioned transmission mechanism 60 is through the parts different from the part of storage space V is formed of lid 42. Output shaft 63 is upwardly and toward the external of shell 40 in the drum shaft of housing body 41 and extends.That is, output shaft 63 It is axial axially consistent with the cylinder of housing body 41.

As shown in Figure 3 and Figure 4, motor chamber 45 is connected to the bottom of housing body 41.Specifically, when in output shaft 63 When axis looks up, motor chamber 45 is attached to housing body 41 at position not Chong Die with output shaft 63.

Motor 50 generates the actuating driving force for activating clutch 13.Motor 50 is arranged in motor chamber 45, so that not The rotary shaft shown axially extends.

Transmission mechanism 60 includes input shaft 61, jackshaft 62 and output shaft 63 (transmission member).Input shaft 61, jackshaft 62 It is arranged in parallel with output shaft 63.Input shaft 61 is the output shaft of motor 50.Therefore, jackshaft 62 and output shaft 63 and motor 50 Output shaft is arranged in parallel.That is, input shaft 61 and jackshaft 62 are along the axially extending of output shaft 63.

One end in the axial direction of input shaft 61 is located in the motor chamber 45 for accommodating motor 50.It is another in the axial direction of input shaft 61 One end is located in the space limited by housing body 41 and lid 42.The other end in the axial direction of input shaft 61 is provided with gear 61a, Gear 61a has the multiple teeth arranged in the circumferential.In this embodiment, gear 61a is spur gear.

One end in the axial direction of jackshaft 62 is pivotally supported in housing body 41.Intermediate gear as spur gear 64 are arranged on jackshaft 62, can rotate together with jackshaft 62.Intermediate gear 64 and the gear 61a phase of input shaft 61 are nibbled It closes.The rotation of input shaft 61 is transmitted to jackshaft 62 by intermediate gear 64 as a result,.That is, jackshaft 62 is according to input The rotation of axis 61 and rotate.

Jackshaft 62 is provided with gear 62a, and gear 62a has the multiple teeth arranged in the circumferential, and gear 62a is arranged in ratio Position of the one end of jackshaft 62 being pivotally supported in housing body 41 closer to the center in axial direction.In the embodiment In, gear 62a is the spur gear than intermediate gear 64 closer to the side in the axial direction of jackshaft 62.

The other end in the axial direction of jackshaft 62 is pivotally supported on lid 42.The other end in the axial direction of jackshaft 62 It is provided with the rotation transfer part 83 of aftermentioned friction mechanism 80.Specifically, the other end in the axial direction of jackshaft 62 is provided with Cross section is the rotation transfer part 83 of rectangle (referring to Figure 13).Jackshaft 62 includes a part (centre for rotating transfer part 83 The other end in the axial direction of axis 62) it is protruded outward from housing body 41.Rotation transfer part 83 is inserted into aftermentioned friction mechanism 80 (referring to Figure 12 and Figure 13) in the through-hole 81a of rotary body 81.As described above, including rotation transfer part 83 by make jackshaft 62 A part be projected into except housing body 41, be easy to determine friction mechanism 80 when friction mechanism 80 is assembled into jackshaft 62 Position.Therefore, the assembling of clutch drive apparatus 14 can be easy to be performed.On the direction of rotation being applied on jackshaft 62 Torque is less than or equal under the case where predetermined value (for example, the case where output of motor 50 stops), and friction mechanism 80 passes through friction Power reduces the rotation of jackshaft 62.

As shown in figure 4, one end in the axial direction of output shaft 63 is pivotally supported in housing body 41, and output shaft Central part in 63 axial direction is pivotally supported on lid 42.The other end in the axial direction of output shaft 63 be projected into lid 42 it Outside.The other end in the axial direction of output shaft 63 is connected to the second arm 34 of link mechanism 16, can revolve together with the second arm 34 Turn.The rotation of output shaft 63 is transmitted to clutch 13, and the clutch generated in clutch 13 by link mechanism 16 as a result, Reaction force is input to output shaft 63 by link mechanism 16.

The output gear 65 of fan-shaped shape is arranged on output shaft 63 with can be with output shaft 63 together in a top view Rotation.Output gear 65 is spur gear and is meshed with the gear 62a of jackshaft.The rotation of jackshaft 62 passes through defeated as a result, Gear 65 is transmitted to output shaft 63 out.That is, output shaft 63 is rotated according to the rotation of jackshaft 62.

As described above, output shaft 63 receives the rotation of the jackshaft 62 of clutch drive apparatus 14, and also receive clutch The clutch reaction force generated in device 13.

One end on the thickness direction of output gear 65 is provided with cylindrical pin 72 outstanding in a thickness direction.Namely It says, pin 72 is upwardly extended in the axis of output shaft 63.In this embodiment, as shown in Figure 3 and Figure 4, axis of the pin 72 in output shaft 63 Upward side is arranged on a surface on the thickness direction of output gear 65.That is, pin 72 is arranged in output gear On wheel 65, so that pin 72 extends towards the bottom of housing body 41, wherein output shaft 63 and output gear 65 are arranged in shell 40 In.Therefore, pin 72 is rotated with the rotation of the output gear 65 rotated together with output shaft 63 around output shaft 63.Pin 72 contacts First protrusion 71b of the spring 71 of aftermentioned auxiliary body 70.Pin 72 can be rotated relative to output gear 65.Therefore, as after Described, when mobile while the first protrusion 71b of the pin 72 in contact spring 71, pin 72 is prominent relative to first while rotating It is mobile to play 71b.

Auxiliary body 70 includes spring 71 (secondary spring component) and above-mentioned pin 72.Spring 71 includes spirally prolonging around axis The wire rod stretched.Spring 71 is in the tubular extended in the axial direction.Spring 71 is so-called torsionspring, by the one end for making wire rod The elastic-restoring force in circumferential direction is generated relative to the other end torsion of wire rod in the circumferential.In this embodiment, spring 71 Wire rod is from winding starting end (the first protrusion 71b) i.e. one end wound clockwise of wire rod, as shown in Figure 6.

When the axis of output shaft 63 looks up, spring 71 is arranged in housing body 41 to surround input shaft 61 in Between axis 62.Input shaft 61 is inserted into spring 71.One end in the axial direction of jackshaft 62 is pivotally supported at housing body 41 In a part (aftermentioned protruding portion 46) inside spring 71.The axis of spring 71 orients in parallel with output shaft 63.Structure One end at the wire rod of spring 71 extends towards output shaft 63.

Fig. 6 is when the view of the schematic configuration of auxiliary body 70 when the axis of output shaft 63 looks up.Such as Fig. 6 institute Show, the column protruding portion 46 on the inner surface of housing body 41 is set and is located inside spring 71.The outer diameter of protruding portion 46 is less than The internal diameter of spring 71.Protruding portion 46 is with the pass through openings 46a being inserted into for input shaft 61 and in the axial direction of jackshaft 62 The opening portion 46b of one end insertion.

Spring 71 contacts a part of the close output shaft 63 of protruding portion 46.It is prominent including the part that is contacted with spring 71 The circumferential part in portion 46 is provided with metallic contact plate 47 out, when the axis of output shaft 63 looks up, the metallic contact plate 47 tool There is arcuate shape.The both ends of contact plate 47 are fixed on the protrusion 46c of protruding portion 46.Spring 71 contacts contact plate 47.Work as spring When 71 operation, the contact plate 47 being arranged on protruding portion 46 can reduce the damage of protruding portion, as described later.

The one end for constituting the wire rod of spring 71 extends towards output shaft 63, as described above.That is, one end of wire rod from Spring 71 extends radially outwardly.The other end of the wire rod of spring 71 also extends radially outwardly from spring 71.That is, spring 71 It include: tubular spring body 71a；First protrusion 71b comprising one end of wire rod and radially outward prolong from spring body 71a It stretches；With the second protrusion 71c comprising the other end of wire rod and extend radially outwardly from spring body 71a.In the embodiment In, when the axis of output shaft 63 looks up, the first protrusion 71b and the second protrusion 71c extend towards output shaft 63.

First protrusion 71b contacts the pin 72 being arranged on the output gear 65 of output shaft 63.Second protrusion 71c contacts shell The inner surface of main body 41.As shown in Figure 7, it is assumed that be located at the position of clutch separation state as described below in output gear 65 In the case of, when the axis of output shaft 63 looks up, the inner space of housing body 41 is by by the axle center P and bullet of output shaft 63 The imaginary line M of center Q (axis) connection of spring 71 is divided into two regions X and Y, as described later, the first protrusion 71b and the second protrusion 71c is located at the different zones in two regions X and Y.That is, as shown in fig. 7, being located at clutch separation in output gear 65 In the state of the position of state, the first protrusion 71b of spring 71 is located in the X of region, and the second protrusion 71c is located in the Y of region.Figure 7 correspond to Fig. 6 and describe the schematic diagram of region X and Y with hacures.

As a result, in spring 71, one end of the wire rod in the first protrusion 71b in the circumferential direction of spring 71 with contact shell It is mobile far from the second protrusion 71c in the first protrusion 71b in the case that second protrusion 71c of the inner surface of main body 41 rotates together Direction on generate elastic-restoring force.That is, in pin 72 so that clutch 13 becomes engaging from clutch separation state The mode of state with the rotation of output shaft 63 and around the axis of output shaft 63 rotation in the case where, the first protrusion of spring 71 71b is pushed in the circumferential direction of spring 71 by pin 72.One end of the wire rod of spring 71 is rotated around the axis of spring 71 as a result, to connect The other end of wire rod in nearly second protrusion 71c.This of spring 71 is deformed so that the first protrusion 71b far from the second protrusion 71c mobile mode generates elastic-restoring force in spring 71 along the circumferential of spring 71.

Fig. 8 shows the schematic diagram of the relationship between the rotation position of output gear 65 and the deformation of spring 71.At these In view, in order to describe, output shaft 63 and output gear 65 are indicated with double dot dash line, and only pin 72 and spring 71 use continuous lines It indicates.In these views, in order to describe, region X and Y is indicated in a manner of being similar to Fig. 7 with hacures.It is attached in order to simplify Figure, Fig. 8 schematically show the region X and Y limited by imaginary line M.

As shown in figure 8, in the case where pin 72 is rotated with the rotation of output gear 65 around the axis of output shaft 63, bullet The one end of the wire rod of spring 71 contacted with pin 72 shifts in the circumferential direction of spring 71 relative to the other end of wire rod.In such case Under, contact point T between the first protrusion 71b of one end of pin 72 and the wire rod including spring 71 along the first protrusion 71b relative to First protrusion 71b is moved back and forth.

Fig. 8 (a) shows the rotation position of the output gear 65 when clutch 13 is in discrete state.Fig. 8 (b) is shown (occur to slide the power on still direction of rotation between clutch disc 23 and friction plate 24 when clutch 13 is in half-clutch state The state being passed) when output gear 65 rotation position.Fig. 8 (c) is the output gear when clutch 13 is in engagement state 65 rotation position.

Specifically, being located at shown in Fig. 8 (a) in output gear 65 and rotating when the axis of output shaft 63 is looked up In the case where position, that is to say, that in the region X that the pin 72 being set on output gear 65 is located in two regions X and Y In the case of, pin 72 contacts at the part by front end with the first protrusion 71b of spring 71, wherein two regions X and Y are logical Cross the imaginary line M of the axle center P of the connection output shaft 63 and center Q of spring 71 inner space of housing body 41 is divided into two and It obtains.

It is to make output gear 65 by the power that the elastic-restoring force of spring 71 is applied on pin 72 as a result, as shown in Fig. 8 (a) (also referred to as make the direction of rotation of clutch separation: by the rotation side of the dash-double-dot arrow meaning in Fig. 8 (a) in predetermined direction To) on rotate so that the isolated power of clutch 13.That is, spring 71 is by pin 72 in the rotation side for making clutch separation Apply torque to output gear 65 upwards.

In the case where Fig. 8 (a), the first protrusion 71b of spring 71 is not moved significantly by pin 72 in the circumferential direction of spring 71 Position.Therefore, in the case where the power being applied on pin 72 by the elastic-restoring force of spring 71 is than aftermentioned Fig. 8 (b) and Fig. 8 (c) Those power are small.For example, pin 72 from the first protrusion 71b of spring 71 receive by solid arrow meaning in Fig. 8 (a) direction and greatly Small power.

In the case where the rotation position shown in output gear 65 is in Fig. 8 (b), that is to say, that be moved to ratio in pin 72 In the case where being located closer to imaginary line M shown in Fig. 7 (a), the first protrusion 71b displacement of spring 71 is one end so that wire rod In the Y of region, that is to say, that one end of the wire rod in the first protrusion 71b is another close to the wire rod in the second protrusion 71c End.For example, pin 72 is close in the case where the position shown in Fig. 8 (a) of output gear 65 becomes position described in Fig. 8 (b) First protrusion 71b of contact spring 71 while spring body 71a.

Spring 71 reverses in the circumferential as a result,.As a result, spring 71 is in the first protrusion 71b far from the second protrusion 71c movement Elastic-restoring force is generated on direction.The elastic-restoring force of spring 71 is applied on pin 72, as the solid arrow in Fig. 8 (b) is signified. That is, the elastic-restoring force of spring 71 as make the direction of rotation of clutch separation (by the double dot dash line arrow in Fig. 8 (b) The signified direction of rotation of head) on torque output gear 65 is transmitted to by pin 72.Make the direction of rotation of clutch separation as a result, On auxiliary force output gear 65 from spring 71 is transmitted to by pin 72.At this point, being applied to pin from the first protrusion 71b of spring 71 Power on 72 is greater than the power in the case where Fig. 8 (a).

In the case where the rotation position shown in output gear 65 is located at Fig. 8 (c), that is to say, that be located at two in pin 72 In the case where in region Y in region X and Y, the first protrusion 71b of spring 71 is shifted by pin 72, with prominent further to second Play the other end of the wire rod in 71c.At this point, pin 72 is located at relative to the first protrusion 71b of spring 71 than position shown in Fig. 8 (b) Set the position closer to one end of wire rod.

The further torsion in the circumferential of spring 71 as a result,.The elastic-restoring force of spring 71 is applied on pin 72, such as Fig. 8 (c) In solid arrow it is signified.That is, the elastic-restoring force of spring 71 is rotated in output gear 65 so that clutch 13 engages Direction (hereinafter referred to as make clutch engage direction of rotation: by the direction of rotation of the dash-double-dot arrow meaning in Fig. 8 (c)) It is upper to be applied on output gear 65 by pin 72.Make as a result, clutch engage direction of rotation on auxiliary force by pin 72 from Spring 71 is transmitted to output gear 65.

When the axis of output shaft 63 looks up, contact point T between pin 72 and the first protrusion 71b of spring 71 according to The rotation of output gear 65 and across the imaginary line M for connecting the axle center P of output shaft 63 with the center Q of spring 71.Contact point T with The distance between the center Q of spring 71 D changes according to the rotation of output gear 65.That is, when the axis in output shaft 63 When looking up, distance D is minimum when contact point T is across imaginary line M and increases with from imaginary line M to the distance of contact point T Increase greatly.

Fig. 9 shows the relationship between the rotation angle (actuator rotation angle) of output gear 65 and shaft torque, the axis Torque are as follows: torque is applied on the direction of rotation on output shaft 63 by operating the load (clutch load) of clutch 13 Torque (hereinafter referred to as shaft torque)；The shaft torque on output shaft 63 is applied to by the auxiliary force of auxiliary body 70；With by clutch Device loads (clutch reaction force) and generates in the shaft torque on output shaft 63 and generate the axis on output shaft 63 by auxiliary force The sum of torque.It is counterclockwise from initial rotational position in output gear 65 when the axis of output shaft 63 looks up in Fig. 9 In the case where rotation, actuator rotation angle refers to output gear 65 relative to initial rotational position (position shown in Fig. 8 (c)) Rotation angle.

The rotating range of output gear 65 is limited by the inner surface of housing body 41.That is, when output gear 65 exists The position that output gear 65 contacts the inner surface of housing body 41 when rotating on the direction of rotation for engaging clutch is output gear Limit rotation position of the wheel 65 on the direction of rotation for engaging clutch.When output gear 65 is in the rotation for making clutch separation It is that output gear 65 makes clutch point that output gear 65, which contacts the position of the inner surface of housing body 41, when rotating on direction From direction of rotation on limit rotation position.

In the case of the embodiment, when the axis of output shaft 63 looks up, output gear 65 according to Fig. 8 (c), In the case where the sequence rotation of Fig. 8 (b) and Fig. 8 (a), actuator rotates angle and increases.

Clutch load be equal to for example when clutch 13 operate when, be applied to clutch from the clutch spring 28 of clutch 13 Reaction force (clutch reaction force) in device driving device 14.

When clutch 13 is switched to discrete state from engagement state, clutch reaction force rotates angle with actuator Increase and increase.On the other hand, the position between the first arm 33 and the second arm 34 of the foundation based on link mechanism 16 and length Lever ratio determined by relationship is applied to the shaft torque on output shaft 63 in the solid line by Fig. 9 (in figure by clutch reaction force Solid line with " being generated by clutch reaction force ") signified predetermined activation device rotation angle becomes maximum.

Lever ratio will be described below.Lever ratio refers to that the axis being applied on the output shaft 63 of clutch drive apparatus 14 turns Ratio between square and the shaft torque being applied in rotary shaft 31.In this embodiment, clutch drive apparatus 14 is relative to hair Motivation 11 and clutch 13 are arranged, as shown in Figure 10 and Figure 11.Figure 10 is when schematically showing from above vehicle 1, The view of engine 11, clutch 13 and clutch drive apparatus 14.Figure 11 is schematically shown from 1 side of vehicle When, the view of engine 11, clutch 13 and clutch drive apparatus 14.In Figure 10 and Figure 11, in order to describe engine 11, Other component is not shown in positional relationship between clutch 13 and clutch drive apparatus 14, and simplifies hair in the accompanying drawings Motivation 11, clutch 13 and clutch drive apparatus 14.

In Figure 10 and Figure 11, arrow L indicates the left of vehicle 1.Arrow R in figure indicates the right of vehicle 1.In figure The rear of arrow RR expression vehicle 1.Arrow U in figure indicates the upward direction of vehicle 1.Forward and backward, left and right refer respectively to when from Drive forward and backward, the left and right when rider's observation of vehicle 1.

As shown in Figure 10 and Figure 11, after top and the engine 11 of clutch 13 is arranged in clutch drive apparatus 14 Side.When from above vehicle 1, the top of clutch 13 and the right side of clutch 13 is arranged in clutch drive apparatus 14 Side.Clutch drive apparatus 14 is arranged so that the left and right directions (transverse direction) axially along vehicle 1 of output shaft 63 extends. Clutch 13 is arranged so that the Top-Bottom direction (vertical direction) axially along vehicle 1 of rotary shaft 31 extends.

Clutch drive apparatus 14 is connected to clutch 13 by link mechanism 16.Specifically, the of link mechanism 16 One end of one arm 33 is connected to rotary shaft 31 and extends towards the left side of vehicle 1.One end of second arm 34 of link mechanism 16 It is connected to the output shaft 63 of clutch drive apparatus 14 and extends towards the bottom of vehicle 1.The regulating mechanism of link mechanism 16 35 are connected to each other the first arm 33 and the second arm 34, and the first arm 33 and the second arm 34 are rotated.The of regulating mechanism 35 One adjustment means 91 and the second adjustment means 92 be connected respectively in a thickness direction plate the first arm 33 and plate second Arm 34.As a result, the first adjustment means 91 and the second adjustment means 92 be arranged so that rod-shaped connecting elements 94 and 95 axis that This oblique.In Figure 10 and Figure 11, the construction of link mechanism 16 is simplified.

In the arrangement of above-mentioned link mechanism 16, lever ratio rt is obtained by following equation, lever ratio rt is to apply Ratio between the shaft torque being added on the output shaft 63 of clutch drive apparatus 14 and the shaft torque being applied in rotary shaft 31. In the equation, lever ratio rt is assuming that obtaining in the immovable situation of inclination of regulating mechanism 35 when link mechanism 16 operates ?.

Rt=cos θ 1 × L2/L1 of 2/cos θ (1)

Wherein, θ 1 be when the link mechanism 16 from the side of vehicle 1 by the second arm 34 relative to rotary shaft 31 The parallel reference line of axis is formed by angle (referring to Figure 11), and θ 2 is when the link mechanism 16 from above vehicle 1 When by the first arm 33 be formed by angle relative to the reference line parallel with the axis of output shaft 63 (referring to Figure 10).In addition, L1 is the length of the second arm 34, and L2 is the length of the first arm 33.

In equation (1), as the angle, θ 1 of the second arm 34 increases, cos θ 1 reduces, therefore lever ratio rt increases.As a result, When the rotation angle of the output shaft 63 of clutch drive apparatus 14 increases, lever ratio rt increases.That is, when and output shaft When the rotation angle (actuator rotation angle) of 63 output gears 65 rotated together increases, lever ratio rt increases.

As actuator rotation angle increases, clutch reaction force increases, and lesser with actuator rotation angle Situation is compared, and in the case where actuator rotates the biggish situation of angle, the increase of clutch reaction force is rotated relative to actuator The increase of angle and it is smaller.On the other hand, as lever ratio rt increases, when clutch reaction force is applied on output shaft 63 When the shaft torque that is generated on output shaft 63 reduce.Therefore, as actuator rotation angle increases, shaft torque reduces.

Due to the above reasons, as shown in figure 9, in the case where actuator rotates the lesser situation of angle, by clutch reaction force The shaft torque generated on output shaft 63 increases with the increase of actuator rotation angle, and when actuator rotation angle is more than When predetermined activation device rotates angle, shaft torque reduces with the increase of actuator rotation angle.That is, shaft torque occurs Change and maximum at predetermined activation device rotation angle.

In this embodiment, in Fig. 9, in the case where actuator rotation angle is less than S, clutch 13 is in joint shape State.On the other hand, in Fig. 9, when actuator rotation angle is more than S, clutch 13 is converted to discrete state from engagement state. In Fig. 9, the actuator that S indicates that clutch 13 is initially separated in the case where actuator rotation angle increases rotates angle, and And it is also represented by the clutch disc 23 of clutch 13 and the engagement of friction plate 24 in the case where actuator rotation angle reduces and terminates The actuator of engagement rotates angle.

In Fig. 9, the range that the shaft torque being applied on output shaft 63 is positive and (is greater than zero in Fig. 9) is that clutch 13 engages Shaft torque range, and the range that the shaft torque being applied on output shaft 63 is negative (less than zero in Fig. 9) is that clutch 13 divides From shaft torque range.

In the case where actuator rotation angle increases, applied by the clutch reaction force generated when operating clutch 13 The shaft torque being added on output shaft 63 starts the actuating that discrete state (S in Fig. 9) is converted to from engagement state in clutch 13 Start to generate at rotation angle.The shaft torque being applied on output shaft 63 by clutch reaction force is by making output shaft 63 The power that rotates on the predetermined direction (hereinafter referred to as make clutch engage direction of rotation) that clutch 13 engages generates.For example, Clutch reaction force is generated by the elastic-restoring force of the clutch spring 28 of clutch 13.

In auxiliary body 70, the rotation (actuating driving force) of motor 50 changes the rotation position of output gear 65, makes It obtains actuator rotation angle to increase, that is to say, that change according to the sequence of Fig. 8 (c), Fig. 8 (b) and Fig. 8 (a).As a result, from spring 71 power being applied on the pin 72 of output gear 65 parabolically change and the maximum at predetermined activation device rotation angle.Knot Fruit, the shaft torque being applied on output shaft 63 by the auxiliary force of clutch drive apparatus 14 by auxiliary force (by " being generated " institute in Fig. 9 The continuous lines of representative are signified) parabolically change and is also rotated in predetermined activation device maximum at angle.

As described above, being applied on the pin 72 of output gear 65, as the auxiliary on the direction of rotation for making clutch separation The size of power, spring 71 elastic-restoring force according to output gear 65 rotation position and change.This is because spring 71 Between first protrusion 71b and pin 72 contact point T is according to the rotation position of output gear 65 and the variation along the first protrusion 71b makes Change from the direction of the first protrusion 71b power being applied on pin 72, and also to be located at the of pin 72 and spring 71 Contact point T and the distance between the center Q of spring 71 D between one protrusion 71b changes.

In this embodiment, as shown in figure 9, passing through the driving of motor 50 and auxiliary body 70, that is to say, that pass through clutch Device driving device 14, the shaft torque being applied on output shaft 63 are mainly the shaft torque (negative value in Fig. 9 for keeping clutch 13 isolated Shaft torque in region).

In this embodiment, as shown in figure 9, auxiliary force exists when clutch 13 is switched to discrete state from engagement state Output shaft is input to from the auxiliary body 70 of clutch drive apparatus 14 before being input to clutch 13 from clutch reaction force 63.On the other hand, when clutch 13 is switched to engagement state from discrete state, make the clutch inputted from clutch 13 is counter After firmly becoming zero, the auxiliary force for being input to output shaft 63 from auxiliary body 70 is become zero.

Specifically, in this embodiment, contact portion and output shaft 63 between clutch disc 23 and friction plate 24 Between power transmission path be configured so that at the time of clutch reaction force is transmitted to output shaft 63 to be input to auxiliary force it is defeated It is different at the time of shaft 63.For example, predetermined gap is arranged between the flange part 29a and pressure member 27 of push rod 29.Exist as a result, Pressure member 27 is moved far from clutch boss 26 to the application of push rod 29 via link mechanism 16 by clutch drive apparatus 14 In the case where dynamic power, to 63 input clutch reaction force of output shaft at the time of as shown above.

In the case where the clutch disc 23 of clutch 13 and friction plate 24 are worn, with the unworn situation phase of these pieces Than clutch 13 becomes earlier at the time of being switched to discrete state (being initially separated operation) from engagement state, and clutch 13 Engagement complete (bonding operation completion) at the time of become later.That is, as the chain-dotted line in Fig. 9 is signified, actuator rotation The value S of gyration reduces.

As described above in the case where the clutch disc 23 of clutch 13 and friction plate 24 are worn, by when above-mentioned Carve to 63 input clutch reaction force of output shaft and auxiliary force, can prevent after the lock out operation of clutch 13 starts and Before the bonding operation of clutch 13 is completed, the generation of the period of the auxiliary force obtained by auxiliary body 70 cannot be used.

In clutch unit 17, even if the case where the abrasion loss of clutch disc 23 and friction plate 24 reaches preset limit Under, there is relationship as described above at the time of inputting auxiliary force and clutch reaction force to output shaft 63.That is, even if In the case where abrasion loss reaches preset limit, when clutch 13 is switched to discrete state from engagement state, auxiliary force from Clutch reaction force is input to clutch 13 and is input to output shaft 63 from the auxiliary body 70 of clutch drive apparatus 14 before.Separately On the one hand, when clutch 13 is switched to engagement state from discrete state, in the clutch reaction force inputted from clutch 13 After becoming zero, the auxiliary force for being input to output shaft 63 from auxiliary body 70 is become zero.Even if in clutch disc 23 and rubbing as a result, In the case that the abrasion loss of pad 24 reaches preset limit, also clutch 13 can be made swimmingly to be switched to engagement state or separation State.

Preset limit can be in design in the period in the service life of expected vehicle 1,1 normal use of vehicle ( Design phase is expected to be used) in the case where clutch 13 abrasion loss, or when clutch 13 is opened during the traveling of vehicle 1 Abrasion loss when beginning to slide.

In addition, in this embodiment, when clutch 13 is switched to discrete state from engagement state, in clutch reaction Power starts after being input to output shaft 63 from clutch 13, and auxiliary force becomes maximum.As described above, being existed by clutch reaction force The shaft torque generated on output shaft 63 becomes maximum at predetermined activation device rotation angle under the influence of lever ratio.Another party Face, as noted previously, as auxiliary force becomes maximum after clutch reaction force starts to be input to output shaft 63, therefore can Actuating driving force needed for effectively reducing actuating clutch by auxiliary force.Thereby, it is possible to by clutch 13 from engagement state Swimmingly it is switched to discrete state.

In addition, when clutch 13 is switched to engagement state from discrete state, it is anti-in the clutch for being input to output shaft 63 Before active force becomes zero, the auxiliary force for being input to output shaft 63 becomes maximum.It is completed as a result, in the bonding operation of clutch 13 Period before, that is to say, that in the period that clutch 13 is half-clutch state, can be inputted to link mechanism 16 enough Auxiliary force.As a result, the period of the half-clutch state in clutch 13, can swimmingly be held by lesser actuating driving force The joint action of row clutch 13.

By above-mentioned construction, as the shaft torque being applied on output shaft 63 by auxiliary body 70 with by being produced in clutch 13 The shaft torque that raw clutch reaction force is applied to the summation of the shaft torque on output shaft 63 rotates angle relative to actuator With lesser value, as the thick line in Fig. 9 is signified.That is, the summation of shaft torque is located in half-clutch region shown in Fig. 9 A certain range (under half-clutch state actuator rotation angle range) in.It is relatively small and stable thereby, it is possible to pass through Shaft torque obtains the half-clutch state of clutch 13 in output shaft 63.The summation of shaft torque is needed for actuating clutch 13 The actuating driving force of motor 50.

That is, as described above, auxiliary force by being generated by auxiliary body 70, clutch 13 can be easily from connecing Conjunction state is switched to discrete state, and can obtain stable half-clutch state.

<friction mechanism>

Then, the construction of friction mechanism 80 will be described with reference to Fig. 3 to Fig. 5, Figure 12 and Figure 13.Figure 12 is the side with amplification Formula shows the view of friction mechanism 80.Torque on the jackshaft 62 for being applied to transmission mechanism 60 along direction of rotation is predetermined value In situation below, jackshaft 62 is maintained at quiet by the friction between rotary body 81 and a pair of of friction plate 82 by friction mechanism 80 Only state.As a result, for example, friction mechanism 80 also can in the case where stopping the driving of motor 50 when vehicle stops Keep the discrete state of clutch 13.

Specifically, friction mechanism 80 include rotary body 81, a pair of of friction plate 82, be arranged in jackshaft 62 one end rotation Turn transfer part 83 and spring 84.Storage space defined in the lid 42 of clutch drive apparatus 14 is arranged in friction mechanism 80 In V.Specifically, also as shown in figure 5, the setting of friction mechanism 80 is between lid main body 43 and storage cover 44.Therefore, in the reality It applies in example, as shown in Figure 3 and Figure 4, friction mechanism 80 is arranged so that transmission mechanism 60 rubs in being located axially at for output shaft 63 It wipes between mechanism 80 and motor 50.Friction mechanism 80 can be made to compact without interfering motor 50 as a result,.

As shown in Fig. 3 to Fig. 5 and Figure 12, the two sides on the thickness direction of rotary body 81 are arranged in a pair of of friction plate 82.? That is a pair of of friction plate 82 and rotary body 81 according to friction plate 82, rotary body 81 and rub on the thickness direction of friction plate 82 The sequence of pad 82 stacks.Each friction plate 82 is hollow disc component.The thickness of the hollow disc component contacted with rotary body 81 On at least one of two surfaces there is coefficient of friction, when the surface contacts rotary body 81, obtained by the coefficient of friction Obtain predetermined frictional force.Specifically, the stainless steel plate component that such as surface is polished is made in each friction plate 82.A pair of of friction plate 82 and rotary body 81 be arranged in lid main body 43 in the first set groove 43a.One in a pair of of friction plate 82 is led with lid The inner surface of first groove 43a of body 43 contacts.

As shown in figure 5, each of a pair of of friction plate 82 has multiple positioning salient 82a on its peripheral part.It is fixed Position protruding portion 82a is arranged in the positioning groove 43b being formed in the inner surface of the first groove 43a, wherein a pair of of friction plate 82 It is arranged in the first groove 43a of lid main body 43.It is this to be configured to reduce a pair of of friction plate 82 with rotary body 81 together Rotation.

Rotary body 81 is metallic disc-shaped component.As shown in figure 13, rotary body 81 has the central part for being formed in rotary body 81 (rotation center) and through-thickness run through the through-hole 81a (opening portion) of rotary body 81.When on the thickness direction in rotary body 81 When observation, through-hole 81a is rectangle.The rotation transfer part 83 of one end of jackshaft 62 is set through through-hole 81a.

When observing in a thickness direction, rotary body 81 has the contact portion in the peripheral part of dish type rotary body 81 81b, and contact portion 81b contacts a pair of of friction plate 82.The thickness of contact portion 81b is greater than the thickness of the central part of rotary body 81. That is, contact portion 81b is prominent from the central part of rotary body 81 on the thickness direction of rotary body 81.Rotary body 81 as a result, Contact portion 81b contact a pair of of friction plate 82, wherein rotary body 81 is arranged between a pair of of friction plate 82.

As described above, one end in the axial direction of jackshaft 62 is arranged in rotation transfer part 83.Transfer part 83 is rotated in transversal Face is the column of rectangle.Rotation transfer part 83 is formed in the through-hole 81a of insertion rotary body 81.As a result, in jackshaft 62 In the case where rotating with the rotation transfer part 83 in the through-hole 81a of insertion rotary body 81, the rotation of jackshaft 62 passes through rotation Transfer part 83 is transmitted to rotary body 81.Therefore, friction mechanism 80 is in the direction of rotation phase with the rotation transmitted by transmission mechanism 60 Frictional force is generated on anti-direction.

In Figure 13, zed is the axis of jackshaft 62.The axial direction that axis Z extends is the axial phase with output shaft 63 Same direction.The statement identical with the axial direction of output shaft 63 of the direction (axial direction) of the axis of jackshaft 62 includes the axis of jackshaft 62 As long as the feelings that the not exactly the same rotation of axial direction to output shaft 63 can transmit between jackshaft 62 and output shaft 63 Condition.

The rotation transfer part 83 being arranged in jackshaft 62 is inserted into the through-hole 81a of above-mentioned rotary body 81, so that rubbing machine Power transfer path of the structure 80 thus with input shaft 61 to output shaft 63 from transmission mechanism 60 separates.That is.Rubbing machine Structure 80 is not included in transmission mechanism 60, but is separated with transmission mechanism 60.

By above-mentioned construction, the moving axially with respect to rotation transfer part 83 in jackshaft 62 of rotary body 81 can permit It is dynamic, while the rotation of jackshaft 62 is transmitted to rotary body 81 by rotating transfer part 83.Even if for example existing as a result, in rotary body 81 In the case where tilting or shift in the axial direction of jackshaft 62, rotary body 81 can also be shifted relatively from rotation transfer part 83.

Spring 84 includes the wire rod spirally extended around axis.Spring 84 is in the tubular extended in the axial direction.Spring 84 is Compressed spring, when being compressed in the axial direction, which generates elastic-restoring force.The setting of spring 84 makes in storage cover 44 It obtains axial axial consistent with jackshaft 62.That is, the axis of spring 84 is in direction identical with the axial direction of output shaft 63 Upper extension.

Spring 84 is arranged so that the axis and a pair of of friction plate of spring 84 relative to a pair of of friction plate 82 and rotary body 81 82 is consistent with the thickness direction of rotary body 81.End thereof contacts a pair of friction plate 82 along axis facing one direction of spring 84 In that friction plate 82 for being axially toward the other end.That is, a pair of of friction plate 82 and rotary body 81 are than spring 84 Closer to rotation transfer part 83.In addition, being connect along that friction plate 82 of axis facing one direction in a pair of of friction plate 82 Touch the inner surface of the first groove 43a of lid main body 43.Spring 84 is in a thickness direction to a pair of of friction plate 82 and rotary body as a result, 81 applied forces.Therefore, a pair of of friction plate 82 and rotary body 81 the inner surface of spring 84 and the first groove 43a of lid main body 43 it Between be pressed in a thickness direction.

By previous constructions, in a thickness direction by being produced between a pair of of the friction plate 82 pressed of spring 84 and rotary body 81 Raw frictional force.As a result, by the frictional force between rotary body 81 and a pair of of friction plate 82, the power for inhibiting rotation is applied to in Between on the rotary body 81 that rotates together of axis 62.Therefore, it is less than or equal to rotation in the power being applied on jackshaft 62 along direction of rotation In the case where frictional force between swivel 81 and a pair of of friction plate 82, frictional force inhibits the rotation of rotary body 81 and jackshaft 62.

As described above, in Fig. 9, by the shaft torque of the auxiliary force generation of clutch drive apparatus 14 and by clutch 13 The sum of shaft torque that clutch reaction force generates (signified by the heavy line in Fig. 9) is consequently exerted at clutch drive apparatus 14 Shaft torque on output shaft 63.In Fig. 9,81 He of rotary body is made by the frictional force between rotary body 81 and a pair of of friction plate 82 The range for the shaft torque that the rotation of jackshaft 62 stops is indicated by double dot dash line.That is, on being applied to output shaft 63 In shaft torque, by being located at by the frictional force between in the range of double dot dash line meaning, rotary body 81 and a pair of of friction plate 82 (be less than or equal to predetermined value) inhibits the rotation of rotary body 81 and jackshaft 62.

In the case where the driving of motor 50 stops, clutch disc 23 and friction plate 24 are received through clutch spring 28 and make Clutch disc 28 and the mutual power of 24 backup of friction plate, so that clutch 13 engages.On the other hand, though motor 50 driving When stopping, the friction mechanism with above-mentioned construction 80 being arranged in clutch drive apparatus 14 stops clutch drive apparatus 14 Transmission mechanism 60 operation.Clutch 13 does not operate as a result,.Therefore, by above-mentioned construction, it can obtain and maintain clutch as former state The self-locking mechanism of the mode of operation (half-clutch state or discrete state) of device 13.

In other words, self-locking mechanism as described above can be input to the output shaft of clutch drive apparatus 14 by being arranged 63 clutch reaction force and auxiliary force are so that the summation of the shaft torque generated on output shaft 63 is predetermined value or less and obtains , as shown in Figure 9.

In addition, as described above, the rotation transfer part 83 of jackshaft 62 is inserted into the through-hole 81a of rotary body 81 allows to rotate Body 81 shifts on the direction in addition to direction of rotation relative to jackshaft 62.Even if for example inclined in jackshaft 62 as a result, In the case of, the rotation of jackshaft 62 can also be for delivery to rotary body 81, wherein prevents the inclination of rotary body 81.In this way, Can be by jackshaft 62 come rotating bodies 81, while ensuring the contact of rotary body 81 with a pair of of friction plate 82.

In addition, being assembled in the rotary body 81, friction plate 82 and spring 84 of the friction mechanism 80 in lid 42 by above-mentioned construction The inside of housing body 41 can be attached to.As a result, it is possible to improve the operability of the assembling of friction mechanism 80.

In addition, the shell for accommodating friction mechanism 80 is made of a part of the lid 42 of clutch drive apparatus 14.This makes The overall construction of clutch drive apparatus 14 is compact.

It include clutch 13, motor 50, output shaft 63 and spring 71 according to the clutch unit 17 of the present embodiment.Clutch 13 include: the multiple clutch disc 23 and friction plate 24 that torque is transmitted by frictional force；And clutch spring 28, pass through bullet Multiple clutch disc 23 and multiple friction plates 24 are connected to each other by property restoring force.Clutch 13 is arranged in transmitting torque Switch between engagement state and the discrete state for disconnecting torque.Motor 50 generates the actuating driving force for activating clutch 13. The actuating driving force generated by motor 50 is passed to clutch 13 by output shaft 63, and is received from clutch 13 and be used as clutch The elastic-restoring force of the clutch spring 28 of reaction force.The auxiliary force of assisted activation driving force is input to output shaft by spring 71 63.When clutch 13 is switched to discrete state from engagement state, before 13 input clutch reaction force of clutch, from Spring 71 is input to output shaft 63.When clutch 13 is switched to engagement state from discrete state, it is input to from clutch 13 After the clutch reaction force of output shaft 63 becomes zero, the auxiliary force for being input to output shaft 63 from spring 71 is become zero.

In above-mentioned clutch unit 17, when clutch 13 is switched to engagement state or discrete state, not only from clutch Device 13 apply clutch reaction force and also output shaft 63 is also entered by the auxiliary force that spring 71 generates.Thereby, it is possible to subtract It is small clutch 13 is switched to engagement state or discrete state needed for actuating driving force.

When clutch 13 is switched to discrete state from engagement state, auxiliary force is in clutch reaction force from clutch 13 Output shaft 63 is input to from spring 71 before being input to output shaft 63.In this case, it is cut in clutch 13 from engagement state When being changed to discrete state, even if clutch reaction force becomes earlier, also at the time of being input to output shaft 63 from clutch 13 Enough clutch reaction force is inhibited to be input to output shaft 63 from clutch 13 before auxiliary force is input to output shaft 63.Namely It says, even if clutch disc 23 and friction plate 24 are worn, can also prevent after the lock out operation of clutch 13 starts, cannot make With the generation of the period of auxiliary force.

In addition, being input to output shaft 63 from clutch 13 when clutch 13 is switched to engagement state from discrete state Clutch reaction force become zero after, the auxiliary force for being input to output shaft 63 from spring 71 becomes zero.In this case, When clutch 13 is switched to engagement state from discrete state, make even if the clutch for being input to output shaft 63 from clutch 13 is counter Become at the time of firmly reaching zero later, can also prevent in the clutch reaction force for being input to output shaft 63 from clutch 13 Before becoming zero, the auxiliary force for being input to output shaft 63 is become zero.That is, even if clutch disc 23 and friction plate 24 are ground Damage can also prevent before the bonding operation of clutch 13 is completed, and cannot use the generation of the period of auxiliary force.This In the case of, the period before the bonding operation of clutch 13 is completed, that is to say, that be in half-clutch state in clutch 13 Period, without generating biggish actuating driving force by motor 50.Thereby, it is possible to easily adjust actuating driving force.

As a result, in above-mentioned clutch unit 17, even if when clutch disc 23 and friction plate 24 are worn, it also can be by clutch Device 13 is swimmingly switched to engagement state or discrete state, to cope with clutch disc 23 and friction in the case where uncompensation is worn The abrasion of piece 24.

In the state that the abrasion loss of clutch disc 23 and friction plate 24 reaches preset limit, in clutch 13 from joint shape When state is switched to discrete state, auxiliary force is before clutch reaction force is input to output shaft 63 from clutch 13 from spring 71 It is input to output shaft 63.When clutch 13 is switched to engagement state from discrete state, output shaft is being input to from clutch 13 After 63 clutch reaction force becomes zero, the auxiliary force for being input to output shaft 63 from spring 71 is become zero.

Even if, also can will be from as a result, in the case where clutch disk 23 and 24 abrasion loss of friction plate reach preset limit Clutch 13 is swimmingly switched to engagement state or discrete state.

When clutch 13 is switched to discrete state from engagement state, it is input in clutch reaction force from clutch 13 After output shaft 63, the auxiliary force for being input to output shaft 63 from spring 71 is maximum.

In general, the predetermined amount of time shortly after lock out operation of clutch 13 starts, is input to defeated from clutch 13 The clutch reaction force of shaft 63 increases with the progress of the lock out operation of clutch 13.On the other hand, in above-mentioned construction In, after clutch reaction force is input to output shaft 63 from clutch 13, auxiliary force is maximum.Even if as a result, from clutch The 13 clutch reaction forces for being input to output shaft 63 increase with the progress of the lock out operation of clutch 13, can also be by foot Enough auxiliary forces are input to output shaft 63.As a result, it is possible to which clutch 13 is swimmingly switched to discrete state from engagement state.

When clutch 13 is switched to engagement state from discrete state, in the clutch for being input to output shaft 63 from clutch 13 Before device reaction force becomes zero, the auxiliary force for being input to output shaft 63 from spring 71 is maximum.

Period before the bonding operation of clutch 13 is completed as a result, that is to say, that clutch 13 be in half from The period of conjunction state can input enough auxiliary forces to output shaft 63.As a result, being in half-clutch state in clutch 13 Period can swimmingly execute the bonding operation of clutch 13 by lesser actuating driving force.

(other embodiments)

The foregoing describe the embodiment of the present invention, but above embodiments are only for implementing example of the invention.Therefore, originally Invention is not limited to embodiment, and can repair as needed to embodiment without departing from the spirit and scope of the invention Change.

In the above-described embodiments, when clutch 13 is switched to discrete state from engagement state, auxiliary force is from clutch Output shaft 63 is input to from the auxiliary body 70 of clutch drive apparatus 14 before 13 input clutch reaction forces.Another party Face becomes when clutch 13 is switched to engagement state from discrete state in the clutch reaction force inputted from clutch 13 After zero, the auxiliary force for being input to output shaft 63 from auxiliary body 70 is become zero.Therefore, in embodiment, for example, in push rod 29 Flange part 29a and pressure member 27 between predetermined gap is set.Alternatively, the regulating mechanism 35 of adjustable link mechanism 16, So that clutch reaction force and auxiliary force are applied to as described above on output shaft 63.That is, in order to obtain this implementation The construction of example, also can be used the regulating mechanism 35 of link mechanism 16.In this case, regulating mechanism 35 makes 33 He of the first arm The distance between second arm 34 is bigger than the distance in normal setting, so that shaft torque shown in Fig. 9 can be used as and pass through clutch Shaft torque that reaction force generates on output shaft 63 obtains.

In the above-described embodiments, not set common device of wear compensation.It, can also be with alternatively, in addition to the construction of embodiment Common device of wear compensation is set in clutch 13.That is, clutch 13 may include the position to pressure member 27 Set the mechanism being adjusted, though so as in clutch disc 23 and the abrasion of friction plate 24, be also prevented from Fig. 9 actuator rotation The value S of angle changes.In the case where wearing generation, device of wear compensation can be arbitrary structure, as long as can repair Value S in positive Fig. 9 is to reduce the influence of the operation of the abrasion of clutch disc 23 and friction plate 24 to clutch 13.

In embodiment, the push rod 29 of clutch 13 by the rotary shaft 31 that is connect with link mechanism 16 main shaft 15 axis It moves up.Alternatively, the output of clutch drive apparatus 14 can also directly be passed in the case where not using link mechanism 16 Pass rotary shaft 31.

Specifically, as shown in figure 14, rotation passes through output of the transmission gear 166 and 167 from clutch drive apparatus 114 Axis 63 is directly delivered to rotary shaft 31.In the following description, component similar with those of above embodiments component is by identical Appended drawing reference is indicated and be will not be described again, and will the different component of those of description and above embodiments component.

First transmission gear 166 is arranged on the output shaft 63 of clutch drive apparatus 114, with can be with output shaft 63 1 Play rotation.The other end in the axial direction of rotary shaft 31 is arranged in second transmission gear 167, can revolve together with rotary shaft 31 Turn.First transmission gear 166 and the second transmission gear 167 are intermeshed in the shell 140 of clutch drive apparatus 114.

The rotation of the output shaft 63 of clutch drive apparatus 114 passes through the first transmission gear 166 and the second transmitting tooth as a result, Wheel 167 is transmitted to rotary shaft 31.When rotary shaft 31 rotates, the gear 31a phase of one end in the axial direction of rotary shaft 31 is set It is mobile for the tooth-strip part 29b being arranged on push rod 29, so that push rod 29 is moved up in the axis of main shaft 15.

In the example depicted in fig. 14, clutch drive apparatus 114 does not include friction mechanism.Alternatively, clutch driving dress Setting 114 may include the friction mechanism with the similar construction of construction with the clutch drive apparatus 14 of above-described embodiment.

In embodiment, output shaft 63 be used as receive clutch drive apparatus 14 output and by clutch 13 generate from The example of the transmission member of clutch reaction force.However, transfer part component can be the component in addition to output shaft 63, as long as should The clutch reaction force generated in the output of component reception motor 50 and auxiliary body 70 and clutch 13, such as exports Illustrated by gear 65 and rotary shaft 31.

In embodiment, even if in the state that the abrasion loss of clutch disc 23 and friction plate 24 reaches preset limit, When clutch 13 is switched to discrete state from engagement state, auxiliary force before 13 input clutch reaction force of clutch from Spring 71 is input to output shaft 63, and when clutch 13 is switched to engagement state from discrete state, it is inputted from clutch 13 To output shaft 63 clutch reaction force become zero after, the auxiliary force from spring 71 becomes zero.However, in clutch disc 23 and the abrasion loss of friction plate 24 at the time of reach preset limit, this relationship can also be unsatisfactory for.

In embodiment, when clutch 13 is switched to discrete state from engagement state, clutch reaction force from from Clutch 13 is input to after output shaft 63, and the auxiliary force for being input to output shaft 63 from spring 71 is maximum.Alternatively, clutch 13 from When engagement state is switched to discrete state, before clutch reaction force starts to be input to output shaft 63 from clutch 13 or it When, the auxiliary force for being input to output shaft 63 from spring 71 can be maximum.

In embodiment, defeated being input to from clutch 13 when clutch 13 is switched to engagement state from discrete state Before the clutch reaction force of shaft 63 becomes zero, it is maximum that 63 auxiliary force of output shaft is input to from spring 71.Alternatively, in clutch When device 13 is switched to engagement state from discrete state, become in the clutch reaction force for being input to output shaft 63 from clutch 13 After zero or when, the auxiliary force for being input to output shaft 63 from spring 71 can be maximum.

In embodiment, clutch drive apparatus 14 will be rotated from input shaft 61 by jackshaft 62 is transmitted to output shaft 63.It is rotated alternatively, input shaft 61 and output shaft 63 can be configured to transmit by direct geared.

In embodiment, clutch drive apparatus 14 includes the exemplary friction mechanism 80 as self-locking mechanism.However, Self-locking function can be realized by other constructions.Clutch drive apparatus 14 can not also include friction mechanism 80 etc. Self-locking mechanism.

In embodiment, clutch drive apparatus 14 includes the motor generated for activating the actuating driving force of clutch 13 50.Alternatively, clutch drive apparatus 14 may include other driving sources that can generate actuating driving force.

In embodiment, in clutch drive apparatus 14, the rotation of input shaft 61 is transmitted to the gear of output shaft 63 61a and 62a, intermediate gear 64 and output gear 65 are spur gears.Alternatively, at least one of these gears can be commutating tooth Wheel, and remaining is the gear of other shapes.All gears can be the gear except spur gear.

In embodiment, input shaft 61 is provided with gear 61a, and jackshaft 62 is also equipped with gear 62a.Gear 61a It can be integrally provided with input shaft 61, or can be the component separated with input shaft 61.Gear 62a can be with jackshaft 62 It is integrally provided, or can be the component separated with jackshaft 62.

In the above-described embodiments, the spring 71 of auxiliary body 70 includes the first protrusion 71b projected radially outwardly.First is prominent It plays 71b and contacts the pin 72 being arranged on output gear 65.That is, in the above-described embodiments, the first protrusion 71b and pin 72 it Between contact point T be located at the radial outside of spring 71.Alternatively, contact point T can be located at the radially inner side of spring.That is, First protrusion can extend to the radially inner side of spring.When the axis in output shaft 63 looks up, output gear can be located at bullet The inside of spring or the outside of spring.

In embodiment, the first protrusion of the pin 72 on output gear 65 and the spring 71 in auxiliary body 70 is set 71b is directly contacted.Alternatively, link mechanism has can be set in output gear, so that a part of link mechanism and the first protrusion 71b Contact.

In the above-described embodiments, it in the state that spring 71 is arranged in shell 40, is seen when in the axial direction in output shaft 63 When examining, the spring 71 of auxiliary body 70 includes the first protrusion 71b and the second protrusion 71c extended towards output shaft 63.Alternatively, the Two protrusion 71c can be upwardly extended in the side different from the first protrusion 71b, as long as the second protrusion 71c can contact housing body 41 inner surface reverses the spring 71 when the first protrusion 71b is shifted due to the rotation of output gear 65 in the circumferential i.e. It can.

In the above-described embodiments, when the spring 71 of auxiliary body 70 deforms so that the first protrusion 71b is close to the second protrusion 71c When, spring 71 reverses in the circumferential, to generate elastic-restoring force.Auxiliary body 70 exports elastic-restoring force, as driving The auxiliary force of dynamic clutch 13.It is generated in camber of spring so that the first protrusion is remote however, auxiliary body can be structured as output The elastic-restoring force mobile from the second protrusion, using as the auxiliary force for activating clutch 13.

In the above-described embodiments, clutch drive apparatus 14 includes auxiliary body 70, which has as torsion The spring 71 of spring.However, auxiliary body 70 is configured to the construction in addition to the spring 71 as torsional spring, as long as auxiliary body 70 can export the auxiliary force for driving clutch 13.

In the above-described embodiments, the cylinder of shell 40 is axial, the axial direction of input shaft 61, jackshaft 62 and output shaft 63, with And the axial direction of spring 71 and 84 is identical direction.Alternatively, the cylinder of shell 40 is axial, the axis of input shaft 61 and output shaft 63 To and the axial direction of spring 71 and 84 can be different from each other.

Above-described embodiment is related to the exemplary motorcycle as vehicle 1, but vehicle 1 can have such as three-wheeled vehicle or Any construction of four-wheel car, as long as the construction includes the clutch drive apparatus for driving clutch.

Description of symbols

1 vehicle

13 clutches

14,114 clutch drive apparatus

15 main shafts

16 link mechanisms

17 clutch units

23 clutch disc (torque transmission member)

24 friction plates (torque transmission member)

27 pressure members

28 clutch springs

32 arms

33 first arms

34 second arms

35 regulating mechanisms

40,140 shell

50 motors (actuator)

60 transmission mechanisms

61 input shafts

62 jackshafts

63 output shafts (transmission member)

64 intermediate gears

65 output gears

70 auxiliary bodies

71 springs (secondary spring component)

166 first transmission gears

167 second transmission gears

Claims (5)

1. a kind of clutch unit comprising:

Clutch comprising by frictional force transmit torque multiple torque transmission members and will be described more by elastic-restoring force A torque transmission member clutch spring interconnected, the clutch allow hand over to transmit the engagement state of torque and break Open the discrete state of torque；

Actuator generates the actuating driving force for activating the clutch；

The actuating driving force generated by the actuator is passed to the clutch by transmission member, and from described Clutch receives the elastic-restoring force of the clutch spring as clutch reaction force；

Secondary spring component will be used to that the auxiliary force of the actuating driving force to be assisted to be input to the transmission member, wherein

When the clutch is switched to the discrete state from the engagement state, the auxiliary force is made the clutch is counter Before being firmly input to the transmission member from the clutch, it is input to the transmission member from the secondary spring component, And

When the clutch is switched to the engagement state from the discrete state, the biography is being input to from the clutch Pass component the clutch reaction force become zero after, the institute of the transmission member is input to from the secondary spring component Auxiliary force is stated to become zero.

2. clutch unit according to claim 1, wherein

In the state that the abrasion loss of the torque transmission member reaches preset limit,

When the clutch is switched to the discrete state from the engagement state, the auxiliary force is made the clutch is counter Before being firmly input to the transmission member from the clutch, it is input to the transmission member from the secondary spring component, And

When the clutch is switched to the engagement state from the discrete state, the biography is being input to from the clutch Pass component the clutch reaction force become zero after, the institute of the transmission member is input to from the secondary spring component Auxiliary force is stated to become zero.

3. clutch unit according to claim 1 or 2, wherein

When the clutch is switched to the discrete state from the engagement state, the clutch reaction force start from The clutch is input to after the transmission member, is input to the described auxiliary of the transmission member from the secondary spring component Power-assisted is maximum.

4. clutch unit according to any one of claim 1 to 3, wherein

When the clutch is switched to the engagement state from the discrete state, the biography is being input to from the clutch Pass component the clutch reaction force become zero before, the institute of the transmission member is input to from the secondary spring component State auxiliary force maximum.

5. a kind of vehicle comprising clutch unit according to any one of claim 1 to 4.